Roving package winding apparatus



Feb. 16, 1965 s. G. FORNES ROVING PACKAGE WINDING APPARATUS 4Sheets-$heet 1 Original Filed April 25. 1951 I u win FIG. 1

PRIOR ART FIG. 4

INVENTOR F a 6 4m n7 0 Feb. 16, 1965 e. e. FORNES ROVING PACKAGE WINDINGAPPARATUS 4 Sheets-Sheet 2 Original Filed April 25, 1961 m R Y r m gm 1m A S Feb. 16, 1965 s. e. FORNES ROVING PACKAGE WINDING APFARATUS 4Sheets-Sheet 3 Original Filed April 25, 1951 FIG Feb. 16, 1965 e. e.FORNES ROVING PACKAGE WINDING APPARATUS 4 Sheets-Sheet 4 7 OriginalFiled April 25, 1961 INVENTOR Gaston G. Fornes BY qzevs mdI UnitedStates Patent 0 3,159,362 RQVHNG PACKAGE WENDTNGAPPARATUS Gaston G.Fornes, (Iharlottesviile, Van, assignor to institute of TextileTechnology, Cherlcttesville, Va, a corporation of Virginia @riginaiapplication Apr. 25, 1961, Ser. No. iilSgiiii, now Patent No. 3,123,970,dated Mar. 10, 1964. Divided and this application (Itch R0, 1963, Ser.No. 318,476

5. laizns. (ill. 57-39) This application is a divisional of pendingapplication Serial No. 105,401, filed April 25, 1961, now Patent No.3,123,970, issued March l0, 1964, and assigned to the same assignee asthe present application.

This invention relates to roving frames used in the production oftextile yarns and, more particularly, to apparatus for winding packagesof roving and the like to produce packages having greater density andstability.

Packages of textile roving are produced on roving frames. The packagesare formed by winding roving on bobbins insuccessive, closely woundlayers. The bobbins are made to reciprocate axially so that the coils ofeach layer are wound seriatim. The amplitude of reciprocation of thebobbins and, hence, the length of each layer of roving are decreasedduring winding to provide package stability. Thus, a completed packageof roving is generally cylindrical with tapered ends so that the endcoils of each roving layer are supported by underlying layers in thepackage. Without this support, i.e. taper, the end coils would unlay andtangle requiring that the package be unwound with difiiculty or evendiscarded.

As is well known, a conventional roving frame cornprises a plurality ofdrafting rolls for attenuating each of a large number of ends of silverso that the number of fibers in cross section is reduced. The ends ofroving are then passed to another part of the frame called the fiyerwhich puts a substantially uniform twist per unit length in the rovingand then winds each end onto its own bobbin. The winding operationconsists in laying the end of a roving on a bobbin in successive layers,each layer consisting of a plurality of relatively closely-spaced coilswound around the bobbin. The twisting and winding operations are bothaccomplished with diiferential rotation between the rotating bobbin andthe flyer which rotates about the same axis as the bobbin.

In order that the coils be laid on the bobbin side by side and insuccessive layers, the roving frame is provided with means which causethe bobbin to reciprocate axially with respect to the flyer. Asmentioned, for stability, a conventional roving frame is also providedwith means which reduce by a fixed and constant amount the arnplitude ofeach successivereciprocation of the bobbin so that successive layers ofroving wound on the bobbin have shorter lengths. The apparatus by whichthe amplitude of reciprocation of the bobbin with respect to the fiyeris governed is called the builder, the construction of which is Wellknown. Ordinarily, the builder is actuated by, and in direct proportionto, motion of the so-called tension gearing.

Economic considerations dictate that as much roving yardage as ispractical be wound on each bobbin. However, machines on which packagesof roving are wound and later unwound are complex and expensive.Increasing package diameter is not practical for obtaining ingreases icecreased yardage per package because major modifications in thesemachines would be required.

In a copending application, Apparatus for Winding Packages of Roving andthe Like, Serial No. 850,639, filed November 3, 1959, now Patent No.3,021,664, I have discussed at length the mathematical relationshipswhich must obtain between builder motion and the increasing diameter ofroving layers being wound on the bobbins, to produce packages withtapered ends. For a detailed analysis, the reader is referred to thatapplication.

Sufiice it to say, at this point, thatin the conventional roving frame,decreases in roving layer length are made directly proportional toincreases in roving layer diameter. The result is, of course, productionof packages of roving having straight-line or conically tapered ends.

Packages with conical tapered ends have been common for many years inthe textile industry. However, recent studies have shown that packageswith convexly curved end tapers have significant advantages. Details ofthese studies are also pointed out in the application referred to.

Experiments with the conical end type packages also indicate that mereincrease in roving tension to provide packages of greater density andgreater yardage per unit volume is not helpful. Aggravated end coilstability problems arise which necessitate decreasing the slope of thetaper, thereby introducing an'offsetting reduction in total packagevolume.

But, wh'en the tapers are made convexly curved, packaged volume andhence package yardage are directly increased. Moreover, studies haveshown that end'coil stability can be enhanced with convex end sectionsby increased roving tension during winding. As a result, packages can beproducedwhich have greater density and stability as well assignificantly increased yardage.

It follows that, to produce packages of roving with convexly curved endtapers, the increases in roving layer diameter must be related toincreasingly disproportionate reduction in roving layer length.Mechanisms which provide this relation automatically in a roving framehave been recently devised. They work very well in producing rovingpackages with the advantageous convex end tapers. i

It is too early to know which type ofthese, mechanisms will becomepopular in the textile industry. However, it

stands to reason that any such mechanism which requires little time toproduce and install; whichrequires small modification of existingframes; which is simple, has few moving parts, and for which maintenanceand replacement do not requireextended roving frame stoppage will bepreferred.

Satisfaction of all the above criteria in one machine probablyrepresents a non attainable goal of perfection. However, I believe Ihave invented apparatus that will satisfy more of these criteria thanhave been satisfied by previous developments and which fall well withinthe practical limits of economics circumscribing the problem.

This invention provides apparatus which may be incorporate-d in existingroving frames to produce roving packages which have convex end tapersand increased 60 roving yardage. The apparatus provided can be readilyincorporated in an otherwise conventional roving frame. Further, themechanism provided comprises relatively simple components which can beeasily fabricated and installed. Installation of the new apparatusrequires only minor roving frame modifications.

, operator attention is required. 7 With this invention roving packagescan be produced with significantly increased volume and yardage.

' of FIG. 3A;

According to the invention, a cam is used to relate the proportionalincreases in roving layer diameter to the required disproportionatereductions in roving layer length. The cam can be generally rounded orgenerally elongate. The important feature is that the cam provided has acamming dimension which changes in successively greater disproportionateamounts with respect to successive, equal increments, in a referencedimension.

Input means are provided for displacement of the cam in the direction orsense of the reference dimension upon completion of each layer ofroving. This displacement is provided in successive, equal increments inproportion to successive increases in roving layer diameter. An outputmeans is then arranged on the cam for actuation in response tocorresponding increasingly disproportionate differences in the cammingdimension. The latter changes are utilized directly for controlling theamplitude of the succeeding bobbin reciprocation.

The input and output means can be hydraulically or mechanicallyactuated. They can also be electrically actuated'in which case a cam assuch is not used, but, an

arrangement similarly utilizing disproportionately related differencesin dimensions is provided.

The apparatus of this invention is easily fabricated and installed. Onlyminor roving frame modifications are required, namely, those ofsubstitution of parts. Apparatus embodying this invention may beprovided for installation in most commercial'roving frames now in use.Frame operation is in the normal manner and no special Convexly-curvedpackage ends can be provided with any desired curve or profile. They canbe made sinusoidal,

V parabolic, cycloidal, etc., by simply substituting cams of differentsizes and contours. Fine adjustments in package profile can beobtainedby providing foraxial or off-set center adjustment of the cam, wheninstalled in the roving frame. Furthermore, withthis invention in use,increased package density is attainable. Higher winding tensions can beused, which further increases package yardage, and the packages producedhave improved stability.

These and other features of the invention will become evident uponreading the following, more detailed descriptions. For clarity,reference will be made'to the drawings in which:

FIG. 1 is a schematic illustration of the builder mechanism of atypical, conventional roving'frame;

FIG. 2 is an illustration of an embodiment'of the present invention,installed in the roving frame of FIG. 1, in which a flat shoe camand'hydraulic means provide builder actuation;

FIG. 3 shows a second embodiment of the present invention in whicha'flat shoe cam and mechanical means provide builder actuation; 1

FIG. 3A is an enlarged elevational view, partly broken away, of a partof the builder mechanism shown in FIG. 3; x

FIG. 3B is a sectional view taken along the line 3B3B FIG. 4 is anillustration of a third embodiment of my invention in whichelectro-mechanical means provide builder actuation; and

FIG S is an illustration of a fourth embodiment'of my invention in whicha flat disc cam is installed to provide builder actuation. I

Inasmuch as the construction and operation of conthose skilled in theart to comprehend the details and features of a preferred embodiment ofthe apparatus I have invented.

In FIG. 1 there is shown at 11 a portion of the bobbin rail of a rovingframe which, as is well known, carries the bobbins and the bobbinrotating mechanism. Also, as is well known, the bobbin rail and all themechanism mounted on it is driven up and down so that the bobbins onwhich roving is being wound are reciprocated axially with respect to theflyers. The flyers rotate with respect to the bobbins to put a uniformtwist per unit of length in the roving and then wind it on the bobbin insuccessive layers, each of which consists of closely wound coils.

In order that the successive layers of roving wound on the bobbins areeach shortened by a predetermined amount to form the appropriate taperedends necessary for stability of the finished package of roving, aconventional mechanism known as a builder is used. To orient the readerand to facilitate understanding of the invention, and the manner inwhich embodiments of it are constructed and operated, there will firstbe given a description of part of a conventional roving frame.

A conventional builder mechanism. comprises a suitable bracket 12mounted on the bobbin rail 11 which moves up and down. This bracket hasa vertical portion 13 in which there are suitable tracks or otherguiding means foran upper jaw 14 and a lower jaw 15. These jaws havesubstantially parallel, elongated vertical camming surfaces 16 and 17,respectively.

A shaft 18, called the builder screw, is provided with two oppositelythreaded portions 20 and 21. The upper jaw 14 is provided with internalthreads which mate with the threaded portion 20 on the shaft 18 and thelower jaw 15 is provided with internal threads which mate with thethreaded portion 21; Thus, because the threads on the portions '20 and21 are oppositely directed, rotation of the shaft '18 in one directionor the other will either close or open the jaws upon each other to theextent permitted by the length of the threaded portions 20 and 21.

Adjacent and parallel to the shaft 18 there is a tumbler shaft 22suitably mounted for rotation about its axison a stationary part of themachine frame. A so-called from the bottom of FIG. 1, thereby insuringthat one or I sectors.

ventional roving frames are well known it will not be necessary .todescribe the entire machine to illustrate the operation of apparatusaccording to my invention. A typi- 'cal roving frame is fully describedand illustrated in Hill:

Cotton Drawing, Combing and Fly Frame Processes, pub- Y lished byInternational Textbook Company of Scranton,

Pennsylvania. Accordingly, I will describehere only' so much of atypical roving frame .as isnecessary to enable the other of the arms onthe builder dog will bear on the camming surfaces.

The tumbler shaft 22 is also positively, but intermittently, driven bythe bevel gear 27 fixed to the upper end of the shaft 22 and the bevelgear 28 fixed to the main drive shaft 30 of the roving frame. As is wellknown 7 the gear 27 is 'a sector gear having teeth in two oppositesectors and' having no teeth in the other two opposite The gear 27 is sooriented on the tumbler shaft 22 that whenone or the other of the armson the builder dog is rotated into position toengage the cammingsurfaces on thebuilder jaws, a toothless sector on the gear 27 isadjacent or under the gear 28 on the main drive shaft so that there isno driving torque transmitted to the tumbler shaft.

Now, as the bobbin rail 11 is driven upward or downward to the end ofits stroke the arm of the builder dog in engagement with thecammingsurfaces on the jaws will overrun the end of the camming surfaceso that there is no longer any resistance to the turning moment exertedon' the tumbler shaft by the spring-loaded camming mechanism 26. Thismechanism then causes the tumbler shaft to turn enough to bring atoothed sector of the gear 27' into engagement with the gear 23 and thetumbler shaft is positively and rapidly driven through nearly a halfrevolution before the next toothless sector of the gear 27 comes underthe gear 28. By this time, however, the spring-loaded camming mechanism26 is again in control of the tumbler shaft 22 and causes the shaft tocomplete the half revolution and bring the other arm of the builder dogto bear on the camming surfaces of the builder jaws. Thus, toillustrate, if the bobbin rail is being driven downward while the arm 24engages the camming surfaces, the tumbler shaft cannot turn until thearm 2 overruns the end of the camming surface 16 on the upper jaw 14.The mechanism 26 and the gears 27 and 28 Will then cooperate to turn thetumbler shaft through 180 degrees so that the other arm 25 on thebuilder dog, which is axially displaced with respect to the arm 24-,engages the cam surface 17 on the lower jaw 15.

Those who are acquainted with textile machinery know that the halfrevolutions of the tumbler shaft also actuate a mechanism whichdetermines the direction in which the bobbin rail is driven. At the sametime that the arm 24 overruns the end of the suriace i6 and the tumblershaft 22 turns through a half revolution, the driving mechanism of thebobbin rail is reversed by conventional means so that the bobbin rail isthen driven upward. The upward travel will continue until the arm 25 onthe builder dog overruns the lower end of the surface 17 on the lowerjaw 15, whereupon the tumbler shaft will again be turned by the cammingmechanism 26 and the gears 2? and 28. The bobbin rail driving mechanismwill be reversed and the bobbin rail will again be driven downwardly.

As is apparent, these changes in direction of the bobbin rail travelresult in the bobbins on all the spindles of the roving frame beingdriven up and down with respect to their respective fiyers which areaxially stationary. With each reversal of direction of travel of thebobbin rail a new layer of roving is wound on each of the bobbins.

As has been previously described each successive layer of roving woundon the bobbin by a conventional roving frame is shortened by apredetermined and constant amount so that when the bobbin is fully woundthe ends of the bobbin have a straight tapered shape. In con ventionalroving frames this is accomplished by turning the builder shaft by apredetermined amount in the direction which causes the upper and lowerjaws 1 and to close upon each other, thus bringing the upper and lowerends of the camming surfaces 16 and 17 closer together. Obviously, theupward and downward strokes of the bobbin rail are then shortened by acorresponding amount, for either the arm 24 will overrun the upper endof the surface 16 sooner than before or the arm :25 will overrun thelower end of the surface 17 sooner than before and cause the directionof travel of the bobbin rail to be reversed.

The conventional way of turning the builder screw by the necessaryamount is to drive the builder screw from the tumbler shaft through agear train which causes the builder screw to rotate through an anglewhich is in fixed and direct proportion to the angle through which thetumbler shaft rotates. This gear train, known collectively as thetension and taper gearing, comprises in order a worm gear 3i fixed tothe tumbler shaft and spur gears 32, 33, 34 and 35. The gear 32 inengagement with the worm 31 is fixed to a shaft which is common to thegear 33. This latter gear engages the gear 34 which is fixed to a shaftcommon to the gear 35. The gear 35 engages the teeth 36 on the undersideof an elongated rack gear 37. The rack gear is mounted on suitableguides so that it may be moved from side to side in FIG. 1.

Merely to orient the reader it is well to state here that this rack gearis also the driving element of a belt shipper mechanism for an endlessbelt which runs between the two cones or conical pulleys in the powertrain of the roving frame. The purposes of this power train are notdirectly relevant to this invention and need not be described in detail.However, the rack itself is also an element in the train of gearsbetween the tumbler shaft and the builder screw.

A suitably mounted vertical shaft 33 carries the gears 49 and ii, theformer of which engages the teeth 42 along the side of the rack 3'7 asseen in FIG. 2. The other gear 41 engages a gear 43 fixed to the builderscrew shaft 18. The gear 43 and screw shaft 18 rotate together, but thescrew shaft is of square cross-section and free to slide axially in anaperture in gear 43 as the shaft oscillates with the bobbin rail 11.

A mechanism of this kind can build bobbins having only straight taperedends. While the taper angle may be changed by changing the various gearratios within the mechanism the machine is incapable of making otherthan straight tapers.

According to one embodiment of the present invention, the buildermembers 12, 13, 14, 15, and 18 are removed and replaced by a newcombination of elements shown in FIG. 2. Taper gear elements 33, d9, 41and 43 may. also be removed as they are not required.

In FIG. 2, hydraulic and mechanical means are used in conjunction with aflat, shoe cam 44. This cam is elongate with camming surfaces 45 and 4-6at its longitudinal edges. The cam is mounted in the roving frame withits longitudinal axis parallel to the rack 37 which drives the beltshipper. The cam is rigidly attached by any strong supporting means to,a roving frame structural member.

The camming surfaces on opposite edges of cam 44 are symmetrical withrespect to the longitudinal cam axis. It is sufiicient, therefore, todescribe one of the edge surfaces since the other is a mirror image ofthe first.

The upper camming surface .45 .is best related to a system of Cartesiancoordinates. In this system, with the horizontal axis parallel to thecam longitudinal axis, a reference dimension will be defined as thelength of the cam. The total length is, for this embodiment,approximately equivalent to the length of the belt-shipper cones. Acumming dimension will be defined as the width of the cam.

With the origin of the coordinate system at the left end of the cam, thedirection of increasing length will be to the right, along thehorizontal axis. Now, for a conical taper on the roving package ends,the function relating ordinates and abscissas of the camming surfacewould be linear. i.e., the function would define a straight line with apositive slope. But, for the convexly curved tapered ends, this functionis not linear.

For the latter case, the camming dimension, the cam width, increases insuccessively increasing increments as the reference dimension increasesin successively, equal increments. Specifically, in the referencecoordinates, the slope of the camming surface is positive and isprogressively increasing.

The builder jaws 49 and S0 of this embodiment are mounted for relativemotion on the member 11 of the frame which reciprocates in synchronismwith the bobbin spindles. They are supported on the bobbin rail Ill by aT bracket 51. Two compression springs 52 and '53 are also mounted onbracket 51 with their axes coincident and parallel to the direction ofreciprocation. The builder jaws have flange portions positioned againstthe outer ends of these springs. The springs, being in compression,provide a biasing force exerted against the flanges which tends to movethe jaws away from each other. These jaws also have elongate surfaces 16and 17 similar to those in the conventional type of builder.

A hydraulic system is provided to drive the builder jaws togetheragainst the direction of the biasing forceof the 7 springs. Thehydraulic system comprises cam follower pistons 54 and cylinders 55, andsimilar drive pistons 56 and cylinders 57. Interconnected between theseveral cylinders is a network of tubing 58. Some of the tubes I 59 inthe network are, of course, flexible to allow for movement of followercylinders 55 as well as reciprocation of the drive cylinders. Also, thetubes and cylinders are filled with an incompressible fluid such as, forexam ple, oil which is commonly used in such systems.

The cam follower cylinders 55 are rigidly mounted on a bracket 47connected to rack 37 for simultaneous movement therewith. The followingpistons 54 are arranged to project against the camming surfaces 45 and46 of the shoe cam with their axes co-linear. The drive cylinders andpistons are mounted on the reciprocating frame member 11 on oppositesides of the builder jaws. The drive pistons 56 project against the jawflanges for moving the jaws together.

Operation of the system depends upon relative motion between the camsurfaces and the followers. At the start the rack is moved to the leftand the followers bear against the narrow part of the cam. As the rack37 moves in successive equal steps to the right, the follower pistons 54are driven apart in directions transverse the direction of thelongitudinal axis of the cam. This action increases the pressure exertedon the fluid in the system which in turn causes the fluid to exert anincreased force on the drive pistons 56. Thus, the flanges and builderjaws are driven together against the biasing forces of the spring.

The biasing force is also important in the reverse direction through thesystem. With this biasing force exerted through the flanges on the drivepistons, the follower pistons are held, at all times, against thecamming surfaces of the shoe cam.

Since thefollower pistons are moved relative to their cylinders only inresponse to the successive changes in the width of the cam, as describedabove, the driving force exerted on the jaws 49and 50 provides forclosing movement of the jaws upon each other by amounts which are indirect proportion to the increasing changes in cam width.

The remainder of the roving frame is of standard construction. The usualbuilder dog rotates 180 upon one arm thereof overrunning a cammingsurface on one of the jaws, which causes the direction of reciprocationof the bobbin spindles to be reversed.

The package end profile which the builder jaws cause to be formed inthis invention is a mathematically exact curve based on considerationsanalogous to that which I havedescribed in the referenced application atpages 17 et seq.

The sine wave, ellipse, parabola, cycloid, involute and circle all haveconvex contours. The study of the properties of these curves to dateindicates that the sine curve permits the use'of a reasonable angle atthe beginning of the innermost layers, and it requires only a moderatechanges in the slope as the package isbuilt. I will indicate herein, howmy invention is adapted to produce an end taper fashioned after the sinecurve to produce pack ages of roving with improved volume, density,stability and yardage.

adapted, by providing cams of different profiles, for production ofconvex end tapers after the fashion of the most advantageous geometriccurve determined for particular roving packages. How this can be donewill be readily apparent to those skilled in the art, after reading howit can be done for the sine curve case:

Along a mid-line of a suitable work piece, measure a distance equivalentto the total length of rack movement.

number of n equal increments.

For the 10" x 5" Saco-Lowell ES. 2 roving frame this distance can bethirty inches. The reference coordinate system is now defined with thex-axis along the measured mid-line with the origin at the left end ofthe measured distance. Thus x will vary between x =0 and x inches.

Next divide the distance (x x into a convenient For illustration I willuse 11:10 but for accuracy in actual fabrication a higher number such asn: 100 should be used. Arbitrarily assigning unity value to x =xtabulate normalized values of x from x to x 1. Thus x fl, x =.1, x =.2,x =.3, and so on to x =l.

Then tabulate corresponding angular values y from y to 3 from therelation of y=arc sin x. Thus y;,'=0, y '=5.7, y =ll.5, y =17.4, and soforth to y =90.

A convenient minimum cam width must next be selected. In the 10." x 5"conventional frame of the example in the copending application referredto, it is seen that the difference in lengths of the inside and outsideroving layers is about 3.5 inches. This means that the builder jaws willmo ve together by this amount or, one builder jaw will move 1.75 inches,along the builder screw.

Therefore a minimum cam width of 2 inches is a convenient value withwhich the maximum width will be around 5 /2 inches.

One can 'now calculate ordinate or y values from y to y for the cammingsurface of the present example from the relation where a= /2 of theminimum cam width or 1 inch, and b y =1.224", y =1.340", and so forth toy =2.750".

These values can be readily checked by slide rule. But,

again, for actual fabrication, accuracy requires that many moreordinates be calculated. Also, the calculations should be done bylogarithms so that ordinate values can be computed to the nearest tenthousandth of an inch.

Now the ordinate values can be plotted on the work piece, by standardtechniques, so that a' series of points (x, y) are located'from (x y to(x y For the cam of the embodiment shown in FIG. 2, the lower camrningsurface 46 is laid out with the same ordinate values. But for thissurface, the ordinate values are plotted in the negative y direction,Le, a series of points .(x, y) are P t from (x0 y0) t n yn)- A smoothcurve is next scribed through each set of points so that the cammingsurfaces can be cut and fin- 60. Continuing study indicates to me thatfor winding difv ferent sizes of bobbns with different roving materials,and

ished by standard machine shop practices. Actually, the cam will. be cuta' few inches longer than the length (x -x so that therewill besufiicient material at each end for mounting purposes and foradjustment. The shape of the. cam, edges over such added end portions isnot critical but there should be no abrupt changes in dimen sions orcurvature as the cutting operation is completed beyondthe cammingsurfaces.

The calculations outlined abovewill produce an exact V sine curveprofile on the cam edges. For practical application, modifications, maybe required before the cam is cut. As was discussed in the copendingapplication previously referred to (at page 19), one modificationrelates to provision of a straight line taper at the ends of the finalroving layers because of the rapidly decreasing radius of curvature ofthe sine curve as it approaches This can be providedin the presentembodiment by 9 scribing on the work piece the straight lines which aretangent to the sine curves at the points These lines are then followedin cutting, from the points of tangency to the end of the cam, resultingin a slightly reduced value for y max. or y Illustrated mathematicallyfor upper camming surface 45, ordinate values beyond the point where Thevalue of y at y:60, which is 2.165, is then substituted in the equationto evaluate constant c. Whence y ==c+(d) (x =)=2.l65=c+(2)(.866), andthe constant c is found to equal .433 inch.

Therefore, for the terminal points of the camming surface where x =l.0(normalized), y =.433-l2(x )=2.433 inches The tangent line can then bedrawn directly between the tan 32 /z=.766

Thus the equation of this line is y=l.0+.766(x) If, for example, thistaper angle is to be maintained for /5 of the roving package layers, theterminal point of this line is (x =.2, y =l.l53).

Appropriate adjustments can be made in subsequent calculations of theordinate values because now if the sine curve is to be followed from xto x,,, the net change in y or (y y )=l.597 inches as compared to 1.526

inches previously. This can be done rigorously by fol-- lowingmathematical reasoning similar to that previously discussed. But I havefound that as a practical measure it is sufi'icient if the two curves,i.e., the sine curve and the initial straight line, are joined in thevicinity of the ordinates at x by a smooth curve. The error introducedwill be less than 7%, which is inconsequential, and may be as little ashalf of that amount it the curve is scribed by a skilled draftsman.

Of course the system of FIG. 2 is equally useful if the followercylinders are rigidly mounted on a structural member of the roving framewith the cam supported for simultaneous movement with the rack. In thiscase the cam 44 is simply reversed end for end from the position shownin FIG. 2.

The arrangements discussed would be for a hydraulic system with amechanical advantage of unity. The areas of the cylinders and pistonscan be provided so that the (y max.-y min.) value could be doubled, forexample, the same. Also, a cam with only one carnmingsurface could beprovided in whichcase onefollower piston would It was indicated at page18 of the copending ap l be arranged connected so as to actuate bothdrive pistons. How to construct apparatus for alternative arrangementssuch as these will be apparent to those skilled in the art.

Table I below is a compilation of the values computed for the sine curveillustration.

*Refcrence point.

Another embodiment of my invention in which a flat shoe cam 69, similarto the shoe cam 44 described above, operates a simple mechanical drivefor closing the builder jaws is shown in FIG. 3. The shoe cam 69 ismounted to be traversed back and forth in the direction of itslongitudinal axis by the reciprocating motion of the rack 37. It is alsomounted for up and down motion with the rail 11.

To provide the back and forth motion and to permit the up and downmotion a pair of vertically extending rods 64 and 55 are fixed at theirupper ends to the rack 37 or an extension thereof. Angled braces as and67 are fixed at their upper ends to the rack 37 and at their lower endsto the rods 64- and $55, for example by brackets 68 and as, to brace therods securely in their intended positions relative to each other. Theshoe cam is equipped at its opposite ends with bracnets 6t and 62. Eachof these brackets has two spaced, coaxial sleeve bearings 63. The rod 64is received iri the bearings 63 on the bracket 61 and the rod 65 isreceived in the bearings 63 on the bracket 62. Thus as the rack movesleft and right the rods which are rigidly fixed to it carry the shoe camwith the rack. As best seen in FIGS. 3A and 3B, a mounting frame '70,having a horizontal support plate '71, is fixed to the rail ll. A guideand actuating rod '72; passes through a vertical aperture in the supportplate 71 and extends in both directions from the plate. Al: is upper endthe rod has fixed thereto an upper cam follower '73 in which is mounteda cam follower roller 74 in a position to engage the upper edge of theshoe cam. A lower builder jaw '75 is fixed to the lower end of the rod'72 and is provided with a camming surface '76 which extends parallel tothe rod '72 and is generally similar in construction and purpose to thecamming surface 17 on the builder jaw 15 previously described. In thisarrangement the upper cam follower bracket 7 3, the rod 72 and the lowerbuilding jaw 75 thus move as a unit.

In this embodiment I also provide a combined lower cam follower bracketand upper builder jaw illustrated at 77. A lower cam follower roller '78is mounted in me bracket part of the member 71 in a position where itcontacts the lower edgeof the shoe cam 65). The member '77 is alsoprovided on its builder jaw portion with a carnming surface '7) whichextends parallel to the surface 7e and is generally similar inconstruction and function to the cam surface 16 on the builder jaw 14,previously described. The member 77 has an aperture through which therod 72 extends but the rod and the member are free to move relative toeach other; that is, the rod simply serves as a guide for the member T7.

An upper compression spring 3% is interposed between the support plate71 and the member 77 and acts to urge the member upwardly. Similarly, alower compression springlll is inserted between the support plate 71 7ing of the stop pins.

and the lower builder jaw 75 and acts to urge the lower builder jaw 75,the rod '72, and the upper cam follower bracket 73 downwardly.

The cam follower rollers 74 and 78 engage the upper and lower edges of-the shoe cam as previously stated the up and down motion of the buildermechanism as it reciprocates with the rail 11.

law closure is provided in successively greater increments as the camfollowers are forced apart by relative, longitudinal cam movement. Thenovel mechanism just described cooperates with the builder dog 23 andthe train of gears 31, 32, 33, 34 and 35 and the rack 36 in aconventional manner.

In athird embodiment of my invention shown in FIG. 4, electromechanicalactuation of the builder drive is used. In this embodiment, thereferencedimension, as defined in the discussion above, is the angle ofrotation which is always the same, through which the builder dog 23rotates upon completion of each successive layer of roving.

' A conventional builder jaw mechanism is used for control of thebuilder dog. The builder dog performs in the usual manner, rotatingthrough successive, equal 180 angles upon one arm thereof overrunning acamming surface on one of the builder jaws.

According to this embodiment, a pair of switches 91 and 2 are providedfor alternate actuation by the builder dog arms. A rack 1th and piniongear W7 are mounted in the frame for rotation of a builder screw shaftto close the jaws. A template 93 on which a plurality of stop pins 94are arranged is atfixed to the rack. The camming dimension, again, asdefined in the previous discussion, of this embodiment relates to'thelongitudinal spac- The longitudinal spacing is'provided in amounts whichhave successively greater differences from one end of the template totheother.

A relatively simple electrical arrangement results when the pins are.aligned as shown in two rows on the template. Solenoids 95 and 96 arethen-mounted on opposite sides of the template with solenoid shaftsprojecting therefrom for engaging the rows of stop pins. In thissituation, the pins of each row are longitudinally staggered.Thesolenoidsare connected electrically to the switches at the builderdog. A tension linkage connected between one end of the rack and astationary part of the frame completes the arrangement.

"and last'stop pins will be equal to'the distance moved by thebelt-shipper rack during winding on the conventional roving frame. Aspreviously stated, for a 10 x 5" frame this distance is thirtytothirty-three inches. The template piece 93 is provided slightly longerthan this distance for convenience in mounting and adjust- Longitudinallocation of. the pins can be established several ways, based on themathematical reasoning described previously. A very convenient method isavailable for this example when the taper gears 97, 98 and 99 providedhave a conventional ratio so that the builder shaft rotates through aconventional total number of turns.

Lay off the total distance above, thirty to thirty-three inches, alongthe template center line. Then divide this distance into 10 equalincrements. Then, starting with 3 :0 at the right, and using the 10increments as a scale, where the last mark, y equals 1.00, the ordinateratios from Table I, can be plotted directly along the center line orreference axis. Thus y =0, y =.063, y =.l28, y =.194 etc., to y -=l.00at the left. Then two straight lines are scribed parallel to and aboveand below the center line. They can be conveniently scribed two inchesapart, each being an inch away from the center line. V

'The y values are then projectedperpendicularly from the center line orreference axis to the outer lines with y values for odd values of nbeing projected to one line and those for even values of n, to theother. The template is then drilled at the intersection of the projec- Itions and the outer lines so the stop pins can be mounted When thebuilder dog 23 rotates, one of the switches is 7 noid when the builderdog again rotates, and so on. 1 Each time the rack is advanced insuccessively greater amounts, as determined by the successivelygreaterlongitudinal spacing between stop pins. As a result, of course,the builder jaws are moved together in successively increasingincrements which is the action required for producing roving packageswith convex curved ends.

I I will describe how a template with stop pins is fabricated so thatthe illustrative sine curve profile can be produced at the bobbins. Forsimplicity, rack 1% is made similar to rack 37 of PEG. 1. Then the totaldistance, between the first in staggered array along the template. canbe welded at the points indicated.)

Again, this is illustrative and many more than 10 pins will be required.Actually if n=tl1e number of layers or roving, n+1 pins are necessary.But the above discussion will be adequate to show how these pins arepositioned. V I

Also, the twomodifications described which provide for straight-lineinitial and final package taper can be readily incorporated in thestop-pin arrangement.

For the initial taper angle argument, taper gears 97 and 9 are selectedso. that subsequent, equal step-move ments of rack 100 willresult inbuilder jaw closure to provide the taper angle desired. This is withinthe skill of the present art. Then the first fifth of the template fromy to y (assuming this initial angle will be previously,v the pins aremounted inthe' alternate positions indicated.

For the straight line taper argument near the end of winding, say beyondy=.60 (specifically, for the last 30 of the sine curve or beyond y=.666on the template), thexremaining length on the template is dividedint'o,,r1'1' .equal increments where m the remaining number ofrovinglayers to be wound. These increments are then alternately'projectedtothe stop-pin lines and the pins are mounted accordingly.

Another important embodiment of my invention, shown in FIG. '5, utilizesthe relation of the previously defined ,referenceandcammingdimensions'in a system ofp-olar coordinates. A rotatable camis used in this embodi- Qment in connection witha chain. drive forturning a conventional builder screw shaft 18 through successive,

ly greater a'rcsupon completion of each successive layerf of roving.

r In this "embodiment a flat cam 105 and a wheel gear 106'are rotatablymounted on a common shaft. The shaft and wheel gear are mounted in theroving frame so that the .wheelJgear engagesthe belt shipper rack (Or,the pins 7 5.3 37. As shown, an extension 107 on the rack can beprovided to simplify location problems in the frame.

The periphery 108 of the cam 165 is of a prescribed contour. Thiscontour is readily explained with reference to a system of polarcoordinates in which the pole coincides with the geometric axis of thecam and in which the polar axis or initial line is positioned coincidentwith the shortest radius of the cam. The reference dimension in thiscase is the angle measured from the initial line (counterclockwise). Thecarnming dimension, as l have defined it herein, is the length of anygiven radius from the pole or center of rotation 113 to the cammingsurface 1&8.

Thus, in this cam, successive radii are of increasing length. Moreover,for any series of successive, equal angular displacements from the polaraxis (or initial line), corresponding successive pairs of radii'havesuccessively greater difierences in length. In other words, forsuccessive, equal changes in the value of the angle from the initialline, the corresponding dififerences in values of the lengths of radii(from the center of rotation to the camming surface) are successivelygreater.

The camming surface contour 1% is advantageously formed as a smoothcurve. This means that succes sive arcs of the contour, which aresubtend equal angles at the center of rotation, are of successivelygreater length. Therefore it the cam is rotated (clockwise in the polarcoordinates defined) through successive, equiangular displacements pasta reference line, corresponding successive arcs which cross that linehave lengths whic differ by amounts which are increasinglydisproportionate to the equal angular displacements.

For appli ation of the changing camming dimension principle in thisembodiment, the cam follower comprises a cable 199 which is wound on thecamming surface. It follows that, as the cam is rotated throughsuccessive, equi-angular displacements by the rack 37 and gear wheel 1%,successively increasing amounts of cable will be wound on the cam. Theouter end of the cable is connected to a chain 119 which drives asprocket 111 'through successively increasing angular displacements uponcompletion of each successive layer of roving. The taper gear train 41and 43, driven by the rotating sprocket shaft, then operates to turn astandard builder screw shaft 18 for closing the builder jaws.

A tension linkage 112 attached to the other end of the chain,for'keeping the chain taut and for resetting the mechanism betweendolls, completes the arrangement.

Fabrication or" a cam for this embodiment will be illustrat d, again,for the Saw-Lowell RS. '2, 10" x 5 roving frame.

First a base circle is selected for the cam. I have used a base circlewith a radius ol 8 inches. A semi-circle of this radius is then laid outon a pattern or directly on a work piece. For the reference system ofpolar coordinates, the center or the circle becomes the pole and, withthe semicircle convex upwards, the initial line, r =8 inches, lieshorizontally to the right.

The semi-circle is then divided into 11 equal arc segments. Again, forillustration, 1 will use'n=l0 although the greater the value of 11selected, the more closely the cam surface will approach the desiredcontour.

Thus, radii are drawn on the pattern at successive equal increments inthe value of an angle 0 (measured counterclockwise from r around thepole). These increments in 6 are equal to rr/ 10 radians. Substituting6/- for x in Table I, we thus have a series of normalized values fromt/1r=0, 9 1r=0.l and so forth to 0 /1r -l.0O.

Next a series of radius ratios, r'/r' are computed from the relation idThe values of these ratios from r' to r are the same as those shown incolumn 3 in Table I. Then a series of values for r from r =0 to r=r canbe obtained from the relation and so on to These values of r are markedalong the successive corresponding radii and a smooth curve is scribedthrough the ends of the radii so the cam can be cut from the Work piece.Actually, the camming surface curve should be continued for a verticaldistance of about two inches at each end so that more than the actualcamis cut from the work piece. This providessuil'icient material forconvenience'in mounting and adjusting the cam inthe frame.

Of course the carnming surface can be provided in-other shapes and withvarious modifications for particular bobbin profiles. The modificationspreviously described for initial and final taper angles can be provided.To do so on the cam illustrated, the mathematical reasoning previouslydiscussed is applicable excepting that the same must be adapted for thepolar coordinate situation.

After the cam is cut, the total length of the cumming surface ismeasured, as with a tape so that a proper chain sprocket-and taper gearratio can be selected. This selection is within the present skills ofthe art and will not be explained further at this point.

A more rigorous analysis for developing the camrning surface is alsopossible if one first selects the taper gear ratio andsprocket pitchdiameter. Then, knowing the total number of turns required for thebuilder shaftduring winding, the total camming surface length isdetermined from the relation S=f21r (pitch radius of the sprocket) (N)where N is the-number of sprocket revolutions.

The'base circle radius is selected and the semi-circle is divided asbefore. Then a series of increasing arc lengths can be computed from therelation In polar coordinates, arc length is the relation: ds =dr (n10)?Subsequent values for r from r=r to r can be de veloped using the twoequations expressed. This analysis can be carried forward by thoseskilled in the mathealso expressed from matics and will notbc developedhere.

- Concerning the electroemechanical embodiment of my invention which Ihave'described, other-very advantageous forms can be. provided. One ofthese alternate forms requires negligible roving frame .modification.

Moreover,---with this alternate form, the long-standard builderjaw-mechanism can be eliminated. The. builder screw means.

7 .Two limit switches are actuation by the limit pins.

gizing.

ber of the frame which reciprocates in synchronism with the bobbinspindles. The axis of the shaft is disposed parallel to the direction ofreciprocation. If necessary, an extension can be provided on the shaftto simplify location problems in the frame. The builder shaft herein isconnected by the standard gear arrangements to the belt shipper rack forrotation. But, it does not have the usual builder jaws connected at itslower end. Rather, a series of limit pins are provided projecting in theradial directions from the shaft. p

The principles of reference and camming dimensions as I have hereinabovedefined are again applied. In this alternate embodiment, the referencedimension relates to the angular spacing between successive limit pins.The limit pins are positioned along radii of successively equal angulardisplacement around the builder shaft.

The camming dimension relates to the longitudinal spacing betweensuccessive limit pins. The longitudinal spacing is provided in amountswhich have successively greater differences from the first pin to thelast. In other words, for illustration, the pins can be setperpendicular to the axis of the shaft, along a line on the surface ofthe shaft which defines a helix of continuously increasing pitch. 7

In this embodiment, two sets of these pins are located on the shaftspaced from each other in opposite longitudinal orientation. The pins ofeach set on the shaft are staggered by an angular amount equivalent toone shaft 1 angular displacement.

A collar can be provided in which the pins are mounted. Such a collarprovides increased circumferential distances for equal angular spacingsbetween pins so that no two pins on one collar will be aligned parallelto the shaft The collar can then he slipped on the shaft and held inpla'cefor movement therewith by ordinary key or set- The switches areelectrically connected to the builder dog solenoidsfor altennate ener-As the builder shaft moves upward a limit-pin will close -the lowerlimit switch at the desired limit of upward travel of the bobbinspindle-s. Closing this switch energizes one of the builder dogsolenoids. The corresponding solenoid shaft is thereby withdravm fromengagement with one of the builder dog arms. The builder dog and tumblershaft are thus freed to rotate through the normal180 arc, until theother builder dog arm engages the second gsolenoidshaft. As has beenexplained, this 180 revolution of the tumbler shaft causes the directionof the bobbin spindles to bere'versed. 7

The builder shaft is rotated as in the normal roving frame, throughsuccessive equal arcs upon each builder then arranged in the frame forAccording to this embodiment, a template with two rows of stop pins,longitudinally staggered as before but with successively equallongitudinal spacing, is provided on a rack adapted for longitudinalmovement by a tension linkage. Solenoid shafts are also arrangedengaging the row of stop pins for limiting rack movement. Limit pins arearranged on the builder shaft as descnibed above. Limit switches areagain positioned for actuation by the limit pins.

In this embodiment, a selsyn generator is mounted on the tumbler shaft,with its rotor rigidly affixed to the shaft. successively greaterdecrements in the amplitude of reciprocation are controlled as before,with the limit switches each being electrically connected to a racksolenoid and to a builder dog solenoid; Each time a limit switch isclosed, therefore, the builder dog rotates 180 and the rack advances,moving the builder shaft through successive equal angular displacements.

A selsyn motor, electrically connected to the genenator, is used in thisembodiment for advancing the be'lt'shipper through successive, equaldisplacements in response to the successive 180 displacements of theselsyn generator rotor on the tumbler shaft.

Still another arrangement is possible,-by using a second selsyn motorgeared to the builder shaft, which permits elimination of the above rackand template and stop pin solenoids. In this arrangement, the limit pinsand limit switches are mounted as before for limiting the amplitude ofreciprocation of the bobbin spindles. Solenoids, energized upon closureof the limit switches, are again used for control of builder dogrotation,

' Operation is as before with the added feature of theone'sel'syn-generator being used to drive two selsyn motors Oneselsyn'm-otor is used to rotate the builder shaft and the other, toadvance the belt shipper as described.

. The selsyn evolutions required are, as is evident from my previousdiscussion, all of successively equal amounts.

Hencethe generator rotor on the tumbler shaft can be used, electrically,to drive thetwo motors which, through appropriate gearing arrangements,displacev the belt-shipper and builder shaft, by successive, equal,prescribed amounts.

Concerning the disc cam embodiment of FIG. 5, one

important additional feature should be described. By,

providing an adjustable mounting apparatus at the shaft on which the cam105 and wheel gear 1% are sup-ported,

the axial position of the cam'can be changed. This means that anoperator, skilled in the-use of these cams, can set a the cam geometricaxis to 'a predetermined positioned-set dog' and tumbler shaftevolution. The builder shaft revolution then places the next limit pinin line for succeeding V actuation of the next limit switch.

. 'The nextli-mit switch is in turn closed when the succeedingrecip-rocation is at its zenith. The next solenoid is energizedand'the builder dog again rotates 180 to reverse the .reciprocatorymotion, and so on. Each time the builder shaft is turned (bysuccessively equal angular amounts) the amplitude of the succeedingreciprocation is reduced. T he differences in relative longitudinalspacing of the limit pins are increasingly disproportionate to "thesuccessive equal displacements of the'builder shaft.

Hence, theamplitude is continuously reduced in successively increasingincrements, which is the action required for production ends. a

of roving pack-ages having convexly curved Still anotherelectro-mechanical embodiment within: the

the directionof reciprocation of the bobbin spindles. Tension gearingandthe belt shipper rack are also eliminated;

from the axisof rotation. With such a degreeof mechanical freedom, fineroving package profile modifications can be obtained whichfurtherincreases theutility of this embodiment. V r V I have describedmy invention indetail. Several embodiments discussed above areillustrative of what "can be accomplished within the scopeof myinvention.

lclaimzf" 1. In a roving frame having shaft and builder dog, forreversing the direction of said reciprocatory movement, and a buildermechanism, in

'cluding a builder shaft, mounted on said member to control theactuationlof said reversing means, said builder dog having a pairofoppositely extending arms adapted for alternate engagement with saidbuilder mechanism,the improvement which comprises a 'rack mounted insaid template mounted on said rack, a plurality of stop pins mounted onsaid template'and projecting therefrom, said pins being successivelyspaced longitudinally of said template, soienoid means mounted adjacentsaid template for periodic engagement of said pins, and switch meanselectribobbins mounted on a member of the frame for reciprocatorymovement with ,respectto flyers,'means, including a rotatable tumblercally connected to said solenoid means for actuating the same, saidswitch means being mounted in said frame, the position of said buildermechanism being adapted to determine the position of actuaton of saidswitch means, and said tension linkage biasing said rack forlongitudinal movement when ever said solenoid means are out ofengagement with said pins.

2. The roving frame combination of claim 1 in which said stop pins arealigned in two longitudinal rows on said template, longitudinallysuccessive pins being laterally staggered in said rows, and one saidsolenoid means is mounted adjacent each of said rows, each of saidsolenoid means having a retractable shaft for engaging said pins.

3. The roving frame combination of claim 2 in which said successive stoppins are spaced at increasingly greater longitudinal increments.

4. The roving frame combination of claim 1 in which said gear meanscomprises a gear train one member of which is disposed engaging saidrack and another member of which has a passage at its center in whichsaid builder i8 shaft is slidably arranged for rotation, said buildershaft and train being rotated by said rack when the same is moved bysaid tension linkage.

5. The roving frame combination of claim 3 in which one said switchmeans is mounted adjacent said builder dog for actuation by one of saidarms and .a second said switch means is mounted adjacent said builderdog for actuation by the second of said arms, said one switch meansbeing electrically connected to one said solenoid means, said secondswitch means being electrically connected to the other said solenoidmeans.

References Cited by the Examiner UNITED STATES PATENTS 2,870,597 1/59Hill 5799 X 2,982,487 5 61 Newton 242-461 3,019,588 2/62 Sanders et al.5799 3,049,859 8/62 Wise 5799 3,108,429 10/63 Heiberg S7-99 MERVINSTEIN, Primary Examiner.

1. IN A ROVING FRAME BOBBINS MOUNTED ON A MEMBER OF THE FREAME FORRECIPROCATORY MOVEMENT WITH RESPECT TO FLYERS, MEANS, INCLUDING AROTATABLE TUMBLER SHAFT AND BUILDER DOG, FOR REVERSING THE DIRECTION OFSAID RECIPROCATORY MOVEMENT, AND A BUILDER MECHANISM, INCLUDING ABUILDER SHAFT, MOUNTED ON SAID MEMBER TO CONTROL THE ACTUATION OF SAIDREVERSING MEANS, SAID BUILDER DOG HAVING A PAIR OF OPPOSITELY EXTENDINGARMS ADAPTED FOR ALTERNATIVE ENGAGEMENT WITH SAID BUILDER MECHANISM, THEIMPROVEMENT WHICH COMPRISES A RACK MOUNTED IN SAID FRAME FORLONGITUDINAL MOVEMENT, A TENSION LINKAGE MOUNTED IN SAID FRAME ANDCONNECTED TO SAID RACK, GEAR MEANS CONNECTING SAID RACK TO SAID BUILDINGMECHANISM, A TEMPLATE MOUNTED ON SAID RACK, A PLURALITY OF STOP PINSMOUNTED ON SAID TEMPLATE AND PROJECTING THEREFROM, SAID PINS BEINGSUCCESSIVELY SPACED LONGITUDINALLY OF SAID TEMPLATE, SOLENOID MEANSMOUNTED ADJACENT SAID TEMPLATE FOR PERIODIC ENGAGEMENT OF SAID PINS, ANDSWITCH MEANS ELECTRICALLY CONNECTED TO SAID SOLENOID MEANS FOR ACTUATINGTHE SAME, SAID SWITCH MEANS BEING MOUNTED IN SAID FRAME, THE POSITION OFSAID BUILDER MECHANISM BEING ADAPTED TO DETERMINE THE POSITION OFACTUATION OF SAID SWITCH MEANS, AND SAID TENSION LINKAGE BIASING SAIDRACK FOR LONGITUDINAL MOVEMENT WHEN EVER SAID SOLENOID MEANS ARE NOT OFENGAGEMENT WITH SAID PINS.